Milling machine



April 9, 1935 L. Ff NENNINGER ETAL l 1,997,338

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MILLING MACHINE l Filed Sept. 29, 1929 14 sheets-sheet 8 gwventof Les-ree F? NENN/Ne-R SOL EINSTEIN April 9, 1935- v l.. F. NENNINGER Er AL 1,997,338l

MILLING MACHINE Filed sept. 2s, 1929 14 Sheets-sheet` 9 %%IWM April 9, 1935.

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MILLING MACHINE r Filedl Sept. 28, 1929 14 Sheets-Sheet l0 IIIMIIIIIIIIIIIIL l, (q I 3mm/0155 N LESTER E NENN'NGEQ SoL E1NSTEN April 9, 1935. l.. F. NENNINGER ET AL ,997,338

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L. F. NENNINGER ET AL MILLNG MACHINE Filed Sept. 28, 1929 14 Sheets-Sheet 13 LESTER F NENN/Nfl SOL E /Ns-rE/N mgm dumm* April 9, 1935. 1 F. NENNINGER Er AL 1,997,338

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Patented Apr. 9, 1935 UNITED s'r'xrlais MILLING MACHINE Lester F. Nenninger and Sol Einstein, Cincinnati,

Ohio, assignors to The Cincinnati Milling Machine Company, Cincinnati, Ohio, a corporation of Ohio Application September 28, 1929, Serial No. 395,928 v 44 Claims.

This invention relates to improvements in machine tools and has particular reference to the actuating mechanism therefor.

One of the principal objects of the present invention is the provision of an improved control mechanism for milling machines or other machine tools which will greatly facilitate and minimize the time required for effecting adjustment of the various parts thereof.

Another object of the invention is the provision of improved power actuable mechanism for most rapidly and selectively determining the rate of actuation of a 'given part of the tool.

A further object of the invention is the provision of machine toolrate adjusting mechanism capable of power actuation to expedite the movement thereof, in which the final setting may be automatically effected to minimize the accuracy and attention vnecessary on the part of the operator in obtaining a given effect.

An additional object of th'e invention is the provision ofa single control member available to selectively effect prescribed rate variations in different portions of the general machine tool drive transmissions.

Other objects of the invention include a simplification of the general drive transmissions, a reduction in the number of intermediate shifts necessary to effect a given range of speed and directional variationsof actuation of a part, the provision of an improved transmission which will permit of selective discontinuance of certain of the operative branches of the transmission while rendering other 'branches thereof constantly available, and of an improved mechanism for effecting differentspindle rotation rates and different translatory movement rates through a combination of automatic, manual and manually controllable mechanism which will greatly facilitate attainment of the ultimate desired results by the operator. r.

Other objects and advantages of the present invention should be,I readily apparent by refer-` ence to the following specification, considered inconjunction with the accompanying drawings-illustrative of one embodiment thereof, but itwill be understood that we may make any modiiications in the specific structural details hereinafter disclosed, Within the scope of the appended claims without departing from or exceeding the spirit of the invention.

Figure 1 is a side elevation of a milling machine embodying the present improvement.

Figure 2 is a rear view thereof. Y Figure 3 is a fragmentary horizontal section illustrating the front' and rear quicktraverse con- Y trol mechanism.

Figure 4 is a fragmentar'yfview in elevation and partially in section as on line 4-'4 of Figure 3.

Figure 5 is a transverse section through the v spindle speed variator box and general clutch control mechanism, as on the line 5-5 of Figure l.

Figure 6 is a fragmentary section through the manual selector clutch control mechanism particularly illustrated in Figure 5.

Figure 7 is a developed sectional view through the spindle drive gearing.v

Figure 8 is a section as on line 8-8 of Figure 12, illustrating the spindle speed control cam.

Figure 9 is al development of this cam.

Figure 10 is a view similar to Figure 8 illustrating the back gear and reversecontrol cam.

Figure 11 is a development of this cam.

Figure 12 is a horizontal section illustrating the operative relation of the control cams specifically illustrated in Figures 8 and 10.

Figure 13 is a detail section illustrating the drive for the speed indicating dial.

` n Figure 14 is a vertical section on line I 4-l4 of Figure 12. e -V Figure 15 is a sectional development of the variable speed drive transmission to the translatable parts of the machine tool such as the saddle, knee and table.

Figure 16 is a vertical section through the feed box.

Figure 17 is a fragmentary view illustrating the coupling of certain of the control members.

Figure 18 is an elevation as on line I8--I8 of Figure 16, showing the interior of the feed change boX.

Figure 19 is a detail section illustrating one of the shifter cams and drive therefor.

Figure 20 is a similar view of the related intergear cam member. Figures 21, 22 and '23- are fragmentary views .of the individual cams,` shifter yokes and gear units controlled thereby,

Figure 24 is a section through the feed box illustrating the action of the actuator-detent as on line 24-24 of Figure 19.

Figure 25 is a corresponding section in a different plane through certain of the control members. Figure 26 is a corresponding view illustrating the operative connection of the shifter-yoke illustrated in Figure 23.

Figure 27 is a development unit of Figure 19.

Figure 28 is a detailed of `the central cam vertical section of the Cal rate changer control train from the front of the machine.

Figure 29 is a detail of the automatic neutralizer.

Figure SOIis a development of one, of the motion transmitting cams;-r

Figure 31 is a development of the control cam particularly illustrated in Figure 20.

Figure 32 -is asidejelevation with parts broken away illustrating the automatic feed drive knockout mechanism. y,

Figure 33 is an` endv elevation of the knockout mechanism shown inyFigure 32.

Figure 34 is a fragmentary'perspective view of the knockout mechanism.

Figure 35 is a fragmentary view'of one ofthe actuator therefor, and- Figure 40 is a fragmentary vertical sectionv through a portion of the saddle illustrating the means for controlling translation of the work supporting table theron.

In the drawings, the principles of the present invention have been shown in a specific embodiment as applied to a milling machine, including a bed A having a column B within which is yjour- -naled a spindle C. The column is provided with ways on which a knee D is vertically movable and in turn supports a saddle E for in and out movement or translation on the knee. A second translatable'unit or table F is mounted'on the saddle, suitable power drive being preferably coupled with the. knee, saddle and table to effect desired translatory movements thereof, so that` the distance between the table and spindle may be varied and. in addition, the work supporting portion of the table may be given translatory movements both Vparallel with and transversely of the axis of cutter spindle C.

ln the drawings, in which similar characters of reference are employed to denote corresponding parts throughout the several views,'the numeral 50 designates a control handle, in this case intended to determine quick traverse movement of a selected part. The handle is carried.A b v` a sleeve 5| mounted in the saddle, within whichvtelescopes .shaft 52 extending rearwardly' from the saddle through a bearing block A53 supported by the knee D adjacent the feed box unit 5g, illustrated as disposed upon the column. Shaft 52 has a pinion 55 meshing with a rack portion on plungerl55 having an additional rack, as at 51, which meshes with a gear 51a operatively connected with a vertical splined shaft 58 which is slidably and ro'.- tatably supported at its upper end by lug 59 of the feed boxand by engagement therewith, at its lower end, of lug 60 on rock shaft GII with groove 02 in member 58, as is particularly illustrated in Figure 28 of the drawings. It will thus be seen that in and out movement of the saddle and lever Saat the'front of the machine in no wise interferes with oscillation thereby of shaft plied for automatic 52, which is also actuable by lever 93 on the knee. Oscillation of this'shaft serves to impart an oscillat-ory movement to shaft 58, which is .trans- V mitted through-the vertical spline or teeth 64 and rod 65, shaft 55a, rock arm 66 and control rod 6l through lshifter 68 (see Figure i8) for alterj and shaft 'i6 to the control mechanisms for the saddle; table and knee.

Journaled in the knee is a spindlell (see Figure 28') actuable by,J handle 18 and coupled l through linkage i9 with shaft 80 having rod lug 8| for-oscillation of shaft 82 slidably keyed as at 83 to sleeve 84 rotatably supported by the bed A of the-machine. The arrangement is such that the shaft 82 may Vmove up and down with the knee and ywith respect to the. sleeve A84. This sleeve bears a cam 85 coupledby pin 86 with shaft 6| for oscillation thereof. -Oscillation of this shaft through lug 60 imparts a vertical or reciprocating movement to member 58 along the side of the column. This reciprocating movement acts through rod 81 to actuate eccentric 88 andv clutch control arm 89. When arm 89 is raised from the neutral position shown in Figure 5, it shifts bell crank 90, moving shaft 9| toward the left.- This couples clutch member 92 (see Figure 16) on shaft 9| with the driven clutch member 93 having worm gear 94 meshing with driven worm 95 of the hereinafter described feed transmission, whereby power is supshifting of the feed rate control cam. I

It will be noted that the connection between bell crank and arm 89'is that of a pin 96 engaged in the slot 91 in the lever, as a result of which downward movement of the lever will. not affect member 90, whose return movement is limited by interengagement of pin 98 thereon with abutment cam. 99 oscillatable by handle |00 on the rear of the feed box. This handle and cam incidentally form' a manual control, when the operator is adjacent the column, for rocking the bell lcrank to render the feed selector control clutch 92-93, just described, effective. Disd posed adjacent and in engagement with another portion of the face. of the cam 99 is pin |0| onbell crank vshifter mechanism. |02 controlling spindle speed selector control clutch |03 on shaft- 55 |04. This clutch unit is designed for interlock'- ing engagement with a second clutch unit |05 having gearportion |06 driven from gearA |01 coupled to worm gear |08 and worm |99.

The spindle drive The general manner of application of .power to the machine and thegearing arrangement,

for'determining the rate of spindle speed, will be best understood by reference to Figure. 7 which is a development of the spindle drive gearing considered in connection with Figure 5 illusprovided with discs I1 intertting with the discs ||8 of clutch member l||9.v The frictional coupling of these parts is controlled by conventional clutch fingers and clutch shifter yoke |2| slidablysupported by shaft H6. In this manner shaft ||6 may be operatively connected with the drive sleeve ||4 for actuation thereof 4or may be disconnected therefrom Without stopping the motor or prime mover Shaft 6 bears the gear couple* selectively engageable with gears |24 and |25 of shaft` |25 and in addition bears a second couplet |21|28 selectively K engageable With gears |29 and |30 of 4shaft |26.

Disposed adjacent shaft |26 is a second spline shaft |3| having slidable thereon the gear cou-A plet |32 and |33 selectively engageable with gear |29 or pinion member |34 of shaft-|26. By this mechanism, by the arrangement of gearing just described, shaft |3| maybe operated from the prime mover at any one of 8 selected speeds.

SuDDOrted adjacent shaft |3| is a stub shaft |35 and a splined shaft |36, The spline shaft |36 bears a wide face fixed 'gear |31 while spline shaft |3| has translatably mounted thereon a gear unit |38 which in one position meshes with the left hand portionof the face of gear |31 and in a rearwardly shifted position meshes with reverser pinion |39 carried by shaft |35 and integral with pinion |40 in permanent mesh with gear |31.

It will thus be seen that direct drive from member |38 to gear |31 will cause rotation thereof in a constant given direction while indirect drive of member |31 through pinions |39 and |40 will cause rotation thereof and thus of the supporting shaft |36 in the opposite direction. Shaft |36 forms the nal drive transmitting member for the milling machine spindle |4| of standard conventional construction suitably journaled in the upper portion of column B.

This spindle has mounted thereon sleeve |42 having the large gear portion |43 and a /lesser diameter gear |44. Shaft |36 bears a translatable unit including .a wide face pinion |45 meshable with gear |434 for transmission of maximum power'to the spindle at a relatively low rate of speed and the larger gear portion |46 interchangeably meshable with gear |44 for actuating the spindle at a higher rate of speed.

The spindle speed control mechanism Sleeve ||4 is provided with a gear portion or ring |41 driving the gear train |48, |49 and |50,

which latter serves-to supply power to Worm |09 for continuous power actuation thereof. This power is adapted to be transmitted through gear |08, pinion |01, clutch |03, shaft |04 and worm This cam (see Figures 8 and 12) is provided with path engaging pin |56 on shifter arm |51, path |58 engaging pin |59 of shifter arm |60 and 'path |6| engaging pin |62 of shifter arm |63.

Arm |51 is suitably coupled:y with gear unit |21 land |28 for translation thereof and arm V|63 with unit |22|23 for effecting its translation.

` the position of unit |45-I46.

by reference to'A Figure 11, that cam tracks |80 mine this speed, selector shaft |04 -(see Figure 14) has gear |69vwhich, through intermediate pinion |10, drives gear |1| for the rotary dial member |12 eo-operating with an index pointer or designation as at |13 to denote the particular gear combination enmesh at a given moment and a shifting from one combination to another. If desired, theshiting may be effected entirely by the power actuation and dependence placed on the sensitivity of control of clutch |03 by the operator.

Preferably, however, cam shaft |53 is provided With a stai' Wheel |14 having notches |15 corresponding in number to the several effective positions of the gears; Co-operatingv with Astar Wheel |14 is a load and re or positioning detent mechanism, including plunger |16 bearing roller |11 urged against the star wheel by spring |18. The force of this spring is such that when the cam has been suiciently rotated to cause the roller to ride over one of the points of the star wheel, ,indicating a partial performance ofthe shifting of the gears by the cam, if power be disconnected the spring urge of roller |11 is suiiicient to continue the movement of the cam and thus the shifting'of the gears until same are in proper mesh. -Consequently, the operator needs merely to hold in clutch |03 until the dial is approaching the desiredA speed adjustment, when the clutch may be released and the' parts automatically will be. continued intoproper driving relation at the speed then indicated by the dial.

Additionalspindle speed and direction control The eight speeds of shaft |3| may be further varied to drive spindle |4| at 16 different speeds y for reverser |38 and cam track |8A| operatively associated with shift'lever |83, for determining It Will be noted,

and |8| are unclosed paths of prescribed amplitude, in place of continuous or endless path form,

and this facilitates control of these units by yan oscillation ofthe cam so thattlie shifting may be made from one side of speeds to the other or for reversal of the spindle Without the necessity of passing through the entire series of Lshifts, as in the case of the main spindle speed con-I trolling cam,` although the continuous rotationV type cam could be substituted if preferred.

The relation of the cam tracks |80 and |8| are such that each has a neutral position whereby each of the units |38 and |45|46 are in a nonengagingposition. A partial rotation of the cam from the neutral position will affect, through cam track |8|, a selection of speed, the speed selected depending upon Whether'the cam is rotated clockwise or counter-clockwise. this selection of speed, the cam track |80 will effect .a given direction but the cam track is such that this given direction will be the same irrespective of which speed is chosen or, in other words, whether the cam is rotated clockwise or counter-clockwise. .A further .partial rotation of Simultaneously with l the cam in the same clockwise or counter-clockwise direction as the first partial rotation will effect a cha-nge of direction or, in other words, a reversal of direction, but at the same pre selected speed.

In the present instance, control of cam |19 has been illustrated as manually effected by handle |84 journaled in the speed box cover |85 and serving of oscillation to rotate bevel gear |85. This gear is in direct mesh with' bevel pinion |81 on shaftA |88 of cam |19 for effecting desired oscillatory movement of this cam. An index |89 on the handle, co-operating with designations as at |90 on the machine, facilitates visual determination of the effective positioning of the gear units by various shiftings of the handle, Cam |19 is provided with a star wheel portion as at |9| having notches |92 for selective engagement by positioning roller |93 on arm |94 actuated as by springr |95. "Ihis, like roller |11, actuates as a combined shifter and detent for completing any movement of the cam initiated by lever |84 and locking the same, and thus the parts C Ontrolled by the cam, in -desired shifted position.

The feed transmission The feed transmission proper is particularly illustrated in Figures and 16 of the drawings.

toV

It includes a rapid traverse transmission operable at a i'lxed rate and a sliding gear transmission variably adjustable to obtain at will any one of sixteen selected feeding rates. The primary shaft of this transmission is shaft |98, which is driven by pinion |91 on sleeve |98 which bears worm |09 being driven as previously described by gear |50 and asociate gear train from the gear member |41 actuated directly coupled with the main drive sprocket I3 of the machine, as particularly illustrated in Figure r1.,- Shaft |95 is splined to slidably receive the'gear couplet 200- 20| and the second couplet 202--203. Disposed adjacent shaft |95 is a second shaft 204 having keyed thereto a gear member 205 for actuation by gear 203. A

second gear unit 206 has a portion 201 for alternative engagement by gear 202 of shaft 96 and a portion 208 engageable by gear 209 of sliding unit 2|0 having a second portion 2| alternatively engageable with pinion 2 |2 of the couplet 2 I3 keyed to shaft 204 and having the large gear 2|4 for engagement with gear 200 of shaft |96. It will thus be seen that by translation of units 200-| and 202203,shaft 204 may be actuated at four different speeds and these may be communicated in turn through unit 2|0 to drive shaft 2|5 at eight different selected speeds.

Disposed adjacent shaft 2 5 is the fourth transmission shaft 2|6 bearing the sliding couplet 2|1 comprising a pinion gear 2 8 for engagement with gear 2|9 on shaft 2|5 and the large gear 220 for engagement with pinion 22| on shaft 2 5, whereby shaft 2|6 may be variably actuated at sixteen different speeds depending on the relative positioning of the severalsliding gear units just re-v ferred to.

Secured in the column portion B" of themachine is a bushing 222 having rotatably mounted thereon a clutch member 1| serving as a support for ring gear' 224 normally locked thereto as by the ball safety devices 225 capable of slippage under heavy load, permitting rotation ofthe ring sleeve porton 228 of the clutch flange member 229. This shaft has centrally splined thereon the clutch spool 59 provided on one end with clutch teeth 23| for interlocking engagement with the teeth 232 of member 1| and at its opposite end has the internal beveled portion 233 designedto operate clutch fingers 234.

When shifted to the right, as viewed in Figure l5, the member 59 interlocks with member 1| to drive shaft 10 and thus through bevel gear 15 the power shaft 16 for control of saddle, table and knee movement at a selected rate of speed. When shifted in the opposite direction, or to the left,

clutch 12 is rendered effective to couple member 13 with the shaft. This member being directly driven through the gear transmission series 235 from gear |50 and that in turn from gear |41 on the main drive sleeve,v serves to actuate shaft 16 at a much higher or rapid traverse rate of speed for fast power adjustment of the shiftable Work supporting members previously referred to.

Feed transmission control Power means are provided for rapid automatic sequential shifting of the several translatable sliding gear units, to vary the final feed rate effective through the feed transmission. The drive for this control mechanism is taken from shaft |95 through gears 235 and 231 to shaft 238, to worm 95 and thus through clutch .S3-92 and shaft 9| to bevel pinion 239 and intermeshing bevel pinion 240 of cam unit 24| (see Figure 19).

The general relationship of the control parts will be best understood by reference to Figures 18-20 inclusive, considered in conjunction with the fragmentary detail and sectional views, Figures 21 to 27. Cam member 24| includes a barrel portion 242 having cam track 243, a barrel portion 244 having the cam path 245 and having the intermediate gear 245. The barrel 244 is notched, as at 241, providing a star wheel portion engaged by roller 248 of spring pressed plunger 249, which serves as a combined actuator and detent to aid 'in completing initiated movement of the cam and to lock the cam and several parts associated therewith in proper adjusted position.

Disposed adjacent cam member 24| is a second cam unit 250 having a pinion 25| meshing with gear 246 for actuation thereby. This unit is suitably supported for free rotation and has the barrel portion 252 with cam track 253 and a second barrel 254 Withcam path 255.

Cam path 243 has engaged therein roller 256 on shift lever 251 co-operating with the spool portion 258 of couplet 2 1 controlling the rate of drive from shaft 2|5 to 2| 6. The second groove 245 on this maincam unit 24| vhas engaged therein roller 259 of shift lever 260. which is in turn connected with the spool portion of sliding unit 2|0 for determination of the rate of driveof shaft .215 over shaft 204. This cam therefore controls the gear unit of the upper half of the sliding gear.

transmission mechanism shown in developmentI in Figure 15.

' The cam path 253 correspondingly receives roller 26| on shift lever 262 controlling the unit` 200-20| while path 255 actuates the shift lever 253 for the unit 202-203. By a comparison of Figures v27 and 3l, which are developments respectively of the control units 24| and 250, it will be noted that there area plurality of definite shiftings of the units 200-20| and 202--203 as respects the shiftings of units 2|0 and 2|1. By these several relative shiftings in proper sequence. as automatically determined by these cams, the sixteen successive progressivefeed changes are effected in their proper sequence depending entirely on the period during -which clutch 92--93 is effective for power rotation of shaft 9| and thus of the shifting mechanism.

It will be noted that shaft 9| is provided with a gear 264 serving, through thel intermediate gearing 265, to rotate dial 266 carried on the lefthand side .of the column and serving to indicate by its rotation the progressive shifting of the gears and the several feed rates as the gears move into mesh. In effecting these movements, the operator manually actuates handle 18 or handle |00, depending on whether he is exercising controlfrom the front of the machine or a point adjacent the column. Either of these handles will serve to rock the shifter arm or bell crank-90, moving shaft 9| to couple clutch 92 and start rotation of the cam control mechanism.

As the dial moves to the selected speed, the handle is released, discontinuing the power actuation of unit 24|, when the final movement is completed by the action of the detent plunger 249 both as to the completion of the shifting and locking of the parts in the selected'shifted position.

Similarly, it will be understood that a `rocking of either the control lever 18 or |00 in the oppo' site direction will cause an actuation of the member |02 and thus an energization of the power shifting means for determining the rate of spindle rotation.

Machine operation control For control of the general operation of the machine, use is made of the lever 268 carried by spindle 269 journaled in the column. This spindle has a sleeve providing a rock'arm 210 coupled by link 21 with shifter yoke 212 engaged with clutch spool |2|. Depression of this lever vshifts the spool, to throw out clutch ||9 and stop the drive .of shaft ||6 and thus the application of power to the spindle. Reverse shifting causes engagement of the clutch when thelparts are held in operative relation, as by spring pressed detent 213. As link 21| is shifted, by depressing lever 268, pin 214 thereon engages arm 215 of rock shaft 216 having pinion 211. in engagement with rack 218 on rod 61, This shifts the rod to the left, as viewed in Figure 18, 4compressing spring 219 and moving\ shifter 68 and member 69 to disconnect the feed clutch 1|23|. These parts are therefore held in inoperative position, preventing power actuation of the feed drive when the spindle is stopped. This, however, in no wiseinterferes with a further shifting of member 68 inthe event that it is desired to employ the continuously running power coupling' of the quick traverse drive as desired.

In addition, it will be apparent from the construction of the machine that the operation of thel clutch ||9 in no wise affects the drive to the feed speed transmission and the power gear shifting control mechanisms for the spindle speed and feed speed transmissions, these being in constant rotation as long as the prime mover is actuated. This results in having the power shifting mechanisms always available whether the cutter and table are moving or not, and also provides for quick and easy intermeshing of the gears ofthe Afeed transmission when rat'e shifts are made by the sliding gears. This adds to the facility and speed of operation of lthe machine.

The provision of means on the lever 21 to disconnect the feed drive to the saddle, table and.

knee when the spindle is stopped and also to prevent reconnection until the spindle is started, operates as a safety device, in that it makes it impossible for the operator to throw in the feed for the work table, for instance, until the cutter spindle and its cutter are rotating, thusinsuring that the cutter will be rotating when the Work is fed into it.

Control of trmslatable units In the performance of various milling operations, the two prime essentials are a cutter such and out movement as when different portions of selected width are to be traversed by the same cutter or when form milling or the like is to be performed. This result is attainable in various types of milling machines by interposition'of a plurality of translatable units or supporting mem- .bers between the cutter and the work support, so

that the movements are effected either by a shifting of the cutter spindle, a shifting of the work, or both. In the present instance, for purposes.

of illustration of the` general principles of the invention, the machine has been shown as comprising a bed A having the column B, on which is slidable a knee D for vertical movement supporting a saddle E for transverse or in and out movement and a table or work support F movable at right angles to the saddle for feeding movement of the work, but it is to be understood that the other forms just referred to are clear equivalent Aconstructions to which the invention is equally applicable. The movement of these parts may be effected by control power transmission trains driven by the prime mover or alternatively by a manual adjustment thereof. The mechanisms involved, in attaining these adjustments and tooling shifts, is particularly illustrated in Figures 37 to 41 inclusive. By reference to Figure 36, which is a development Vof the gearing transmissions involved, it will be noted that spline shaft 16 has slidable thereon pinion 282 meshing with gear 283 driving the beveled gears 284-285 transmitting power to spur gear 286 on shaft 281. Spur gear 286, in turn drives gear 288 meshing with the wide face gear 289 directly driving the transmission gear 290 rotating on bushing 29| surrounding spline shaft 292. The Wide face gear 289 also drives reverser pinion 293 meshing with gear 294 rotatable on bushing 295, also surrounding Gears 290 and 294 are thus concentrically located but driven in'opposite directions.

shaft 292.

They have respectively the clutch faces 296 and 291 selectively engageable by clutch 298 having opposite clutch faces,'when moved from its intermediate neutral position. Shaft 292 bears the beveled pinion 299 manually actuable by meshing pinion 299 on shaft 30| which projects diagonally toward the rear of the machine and is adapted to receive actuating handle 362. Keyed or splined within pinion 299 is the feed screw 303'operating in nut 304 carried by the saddle E Consequently, rotation of the pinion by handle 302 or drive power actuation thereof through gear 290 or 294 and clutch 298 will serve lto impart desired in or out transverse movement of the saddle on the knee. In addition, the screw has an extended terminal portion 305 projecting at the front of the machine and bearing the manually actuable wheel 306. The screw may therefore be controlled and manually rotated from an operating position at the front side or edge of the table or from an operating position or station atl the rear edge or column sides of the table.. In general, shifter yoke 301 engages the clutch mem'- ber 298.` This shifter is carried by a sliding rod 338 having a groove therein at 309, 3|0 and 3| l.

' Groove 309 receives a rib 3|2 on rod-3|3 actuable through beveled gears 3| 4 and 3|5 and handle 3|6, which is disposed on the knee in a position accessible from the rear of the table. Groove 3| receives a similar rib 3|1 on rod 3|8 actuable by handle 3|9 at the front of the table. Groove 3|0 receives rib 320 of rod 32| actuable by a dog controlled plunger 322 for controlling the feeding movement of the saddle in either direction.

It will be understood that oscillation of either rod 3|3V or 3|8, by its respective handle, or rod 32| by the plunger aforesaid will impart a longitudinal sliding movement to rod 308 and :its associated shifter. The position of. the handles is such that an oscillation of either, in the direction of the column, will cause a corresponding move.- ment of the saddle, while an oscillation in the opposite direction will cause an outward movement of the saddle with respect to the column, so that.directional control of .the said translatable unit may be effected from either the front or the rear of the table.

The knee ing spline shaft 325, which bears the intermediate clutch member 326 selectively engageable with clutch face 321 of gear 323 or 328 of gear 324.

' thereof. Gear 33|, in addition, has meshing This spline'shaft is provided with a bevel pinion hating the presence of interfering handles and compacting the opera-ting space. It will be un derstood, however, that special 'non-interfering handles or actuating members may be permanently associated with each ofmembers and 345 if preferred.

The drive for translation of the table is effected through spline shaft 346, which supports and'is driven by gear 288 and has slidable thereon beveled pinion 341 meshing with pinion 348 `cn vertical shaft 349 terminating in a beveled gear' 350. 'Ihis gear, for ease of understanding, has been shown in' distorted posit-ion in Figure 40, as distinguished from its actual position indicated in Figure 36. Overlying the'shaft 349 and gear 350 is the table lead screw non-translatably secured, as at 352, in a depending portion 353 of the table F. This screw extends through the nut 354 carried by saddle E. Rotation of the screw in the nut 354 will therefore cause its longitudinal movement, shifting with the table unit.

4This rotation is eiected through a spline sleeve 355 havingr in turn splined thereon clutch 356 selectively engageable with the inner clutch faces of beveled gears 351 or 358,`1oosely rotatable on spline sleeve 355 and in driving engagement with beveled gear 350. This mechanism is such that gears are driven in opposite directions so that shifting' of the clutch member from its neutral positin to the right or left will respectively cause a righthand or lefthand movement of the table. This shifting is effected by yoke 359 on rod 360v terminally notched as at 36| to engage the head of. rock lever 362 actuable by handle 363. In addition, a. second rock lever 364. has a shifter head engaged in notch 365 of the rod and is connecte. ed by link 366 with actuating` handle 361 Vat the front of the machine. In this instance, also, we have manually controlled members for the power translation of the unit located respectively for effecting these movements from operating stations at the front and at the rear of the machine 4so that any selected power actuation of the several translatable units such as knee, saddle and table may be directionally attained by a correv spondingdirectional shifting ofl a control member 'when the operator is at either operating station 329y engaging the beveled gear 33| on n'ut 330 carried by the knee and circumscribing the knee adjusting screw 332. By shifting of the clutch, power vertical adjustment of kneeA D may be eiected through this transmission. The clutch member 326 is controlled by yoke 333 on shift rod 3,34v movable through connection 335, rod 336 and handle 331 at the front ofthe machine or correspondingly longitudinally shiftable through The handles 331 and 340 normally occupy horias respects the machine. In-addition, the table screw is provided'with a hand operating member as at 368, which is accesible from either station. l i

supplementing these control-members, attenf' tion is invited to the-fact that the co-operating levers 50 and 63, respectively, at the front and rear stations. facilitate control from either of these positions of the coupling of feed orv rapid traverse to the' transmissionshaft at the side of the. column for transmissionof the one or the *other of these rods to the several translatabler connection 338. rody 339.and handle 340 at the A `rear, all as particularly illustrated in Figure 38.

it will shift the clutch, to cause a'downward f movement of the knee and, similarly, when raised will cause a power actuated upward movement therewith pinion 34| on rod 342 terminating at the front of the machine by a manually lalctuable handle 343'. A second pinion 344, meshing with gear 33| has an operating rod 345 extending diagonally toward the rear of the machine for suitable manual actuation at that point. In use, handle 302 is normally interchangeably fitted on one or the other of rods 30| and 345, thus elimiunits, while the levers 18 and |00, available at the y6 respective stations, permit selective power shift ing or variance of the variable speed transmission to the spindle or the variable speed transmission of feeding drive to the translatable parts from the operating stations at the front and at the rear of the machine.

"Further attention is invited to the fact that a most compact and efficient mechanism has been provided, in that the single member 58, by diiferent actuations thereof, serves a three-fold purpose, in' that one actuation e'e'cts the power shift-ing mechanism for selection of the rate-of rotation of the tool support or spindle, a second p selective actuation thereof renders effective the power means for determining vthe rate of rotation 

